Hub-less and nut-less turbine wheel and compressor wheel designs and installation/removal tool

ABSTRACT

A forced induction device for an internal combustion engine is provided, which includes a shaft, and a compressor wheel that is threadably mounted to the shaft, and a tool that is configured to engage one or more through bores in the compressor wheel to thread and unthread the compressor wheel onto and off of the shaft. The compressor wheel has a plurality of blades with leading edges that converge at an apex. The apex is aligned with a centerline of the shaft. The tool allows a technician to rotate the compressor wheel relative to the shaft to install or remove the compressor wheel from the shaft without applying any pressure to the blades of the compressor wheel. An associated assembly method is also provided.

CROSS-REFERENCE TO RELATED APPLICATIONS

This is a continuation-in-part application of U.S. patent application Ser. No. 16/710,798, which was filed on Dec. 11, 2019, which is a continuation-in-part of U.S. patent application Ser. No. 16/413,952, now U.S. Pat. No. 10,914,231, which was filed on May 16, 2019 and claims the benefit of U.S. Provisional Application No. 62/720,212, filed on Aug. 21, 2018. The entire disclosures of the above applications are incorporated herein by reference.

FIELD

The subject disclosure generally relates to forced induction devices for internal combustion engines, such as turbochargers and superchargers. More particularly, improved turbine/exhaust wheel and compressor/intake wheel designs are disclosed, which improve fluid flow to increase horsepower without changing the wheel diameter or geometry.

BACKGROUND

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

Forced induction devices, such as turbochargers and superchargers, increase the efficiency and power output of an internal combustion engine by forcing extra air into the combustion chamber compared to naturally aspirated engines. Turbochargers and superchargers are used in a wide variety of internal combustion engines, including gas, diesel, alcohol, and methanol fueled engines, to increase intake air flow with a resulting horsepower gain/advantage.

There remains a need for improvements to forced induction devices, including quicker spool-up, lighter weight, and increased air and horsepower output. This is particularly true for engines used in high performance motorsports including sled pulling, street racing, and drag racing, where high engine speeds and high boost applications are desired and where rules and regulations are often in place that limit the size of the forced induction devices fitted to high performance motors.

Traditional forced induction devices often include compressor and/or turbine wheels with tool interfaces that obstruct the airflow through the device to some extent. For example, traditional turbochargers have a large hex nut (or other style nut or fastener) on both the compressor/intake wheel and turbine/exhaust wheel. This feature, which is incorporated into the “hub” of the compressor/intake wheel and turbine/exhaust wheel, is used during the manufacturing process for many purposes (holding, fastening, tightening, etc.). For example, the hex nut can be used as a clamping device when assembling the turbocharger, during machining operations, and/or during welding processes. After assembly, this hex nut provides no functional purpose to the operation of the turbocharger. The compressor wheels of centrifugal superchargers typically have similar features.

SUMMARY

This section provides background information related to the present disclosure and is not necessarily prior art.

In accordance with one aspect of the subject disclosure, a forced induction device for an internal combustion engine is provided. The forced induction device includes a compressor wheel threadably mounted to a shaft. The shaft is rotatable with respect to a housing and defines a centerline. The compressor wheel has a plurality of blades with leading edges that converge at an apex. The apex is aligned with the centerline.

In accordance with another aspect of the subject disclosure, the compressor wheel includes a body that extends along the centerline between a leading end and a trailing end. The body has an outer circumference that is radially spaced from the centerline by a compressor radius. The plurality of compressor blades are positioned on the body of the compressor wheel. The compressor apex is located at the leading end of the body and is aligned with the centerline of the body of the compressor wheel.

In accordance with another aspect of the subject disclosure, the compressor wheel includes one or more through bores that extend through the compressor wheel at locations that are offset from the centerline of the shaft. A tool is provided with one or more posts that are configured to be received in the through bores of the compressor wheel in a sliding fit. As such, the tool allows the compressor wheel to be rotated and threaded onto the shaft during a compressor wheel installation process and unthreaded from the shaft during a compressor wheel removal process without applying pressure to the compressor blades, which can bend, chip, crack, or break if excessive pressure is applied.

In accordance with another aspect of the subject disclosure, a method of constructing a forced induction device is provided. The method includes the steps of: machining a compressor wheel having a plurality of compressor blades, creating leading edges on the plurality of compressor blades, and performing a finishing operation on the compressor wheel to form an apex where the leading edges converge.

The method further includes the step of temporarily locking the compressor wheel in rotation with a tool that includes one or more posts that are received in one of more through bore in the compressor wheel. The method also includes the step of mounting the compressor wheel to a shaft by inserting the shaft into an internally threaded bore in the compressor wheel and rotating the compressor wheel relative to the shaft in a first direction using the tool to thread the shaft into the internally threaded bore of the compressor wheel.

The nut and/or the nose of the hub on traditional turbine and compressor wheels creates a disturbance in the flow pattern and flow volume of the fluid passing through the turbine and the compressor. This limits horsepower potential. To increase power output, manufacturers typically up-size the frame of the turbocharger or supercharger. The present disclosure advantageously allows for increased power output and efficiency while using the same frame size by eliminating the nut/fastener/hex on the nose of the hub. The strength of the blades does not lie within the center of the hub/shaft so removing the nut/fastener/hex on the nose of the hub does not compromise the structural integrity of the turbine wheel or the compressor wheel.

The designs set forth herein thus provide greater horsepower output and throttle response by modifying the compressor/intake and turbine/exhaust wheels either in conjunction with each other or independently. The elimination of the large hex nut on the hub decreases weight, back-pressure, increases spool-up speed, increases wheel blade length, and alters wheel blade geometry. The flow obstruction created by the hex nut is eliminated to maximize fluid flow and blade length, which can significantly increase horsepower by 10 to 75 percent over conventional fastener nosed hub designs. In addition, the forced induction devices described herein provide improved serviceability because the compressor wheel can be installed on and/or removed from the shaft without applying pressure to the compressor blades, which can bend, chip, crack, or break if wrenched upon.

BRIEF DESCRIPTION OF THE DRAWINGS

Other advantages of the present invention will be readily appreciated, as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

FIG. 1 is a perspective view of an exemplary turbocharger;

FIG. 2 is a side elevation view of a traditional turbine/exhaust wheel for the turbocharger shown in FIG. 1 ;

FIG. 3 is a front elevation view of the traditional turbine/exhaust wheel shown in FIG. 2 ;

FIG. 4 is a side elevation view of an exemplary nose-less turbine/exhaust wheel for the turbocharger shown in FIG. 1 where the exemplary nose-less turbine/exhaust wheel has been constructed in accordance with the teachings of the present disclosure;

FIG. 5 is a front elevation view of the exemplary nose-less turbine/exhaust wheel shown in FIG. 4 ;

FIG. 6 is a side elevation view of a traditional intake/compressor wheel for the turbocharger shown in FIG. 1 ;

FIG. 7 is a side section view of the traditional intake/compressor wheel shown in FIG. 6 ;

FIG. 8 is a front elevation view of the traditional intake/compressor wheel shown in FIG. 6 ;

FIG. 9 is a side elevation view of an exemplary nose-less intake/compressor wheel for the turbocharger shown in FIG. 1 where the exemplary nose-less intake/compressor wheel has been constructed in accordance with the teachings of the present disclosure;

FIG. 10 is a side section view of the exemplary nose-less intake/compressor wheel shown in FIG. 9 ;

FIG. 11 is a front elevation view of the exemplary nose-less intake/compressor wheel shown in FIG. 9 ;

FIG. 12 is a front elevation view of another exemplary nose-less intake/compressor wheel;

FIG. 13 is a front perspective view of an exemplary intake/compressor wheel and backing plate sub-assembly of the turbocharger shown in FIG. 1 ;

FIG. 14 is a front perspective view of an exemplary intake/compressor wheel and a corresponding installation/removal tool, which have been constructed in accordance with the teachings of the present disclosure;

FIG. 15 is a front elevation view of another exemplary nose-less intake/compressor wheel; and

FIG. 16 is a front perspective view of another exemplary intake/compressor wheel and another installation/removal tool, which have been constructed in accordance with the teachings of the present disclosure.

DETAILED DESCRIPTION

Referring to the Figures, wherein like numerals indicate corresponding parts throughout the several views, a forced induction device is illustrated for use with an internal combustion engine (not shown). In the Figures, the forced induction device is depicted as a turbocharger 20, for illustration purposes. However, it should be appreciated that the teachings of the present disclosure also apply to other forced induction devices, including without limitation, centrifugal superchargers.

Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.

The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting. As used herein, the singular forms “a,” “an,” and “the” may be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms “comprises,” “comprising,” “including,” and “having,” are inclusive and therefore specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order discussed or illustrated, unless specifically identified as an order of performance. It is also to be understood that additional or alternative steps may be employed.

When an element or layer is referred to as being “on,” “engaged to,” “connected to,” or “coupled to” another element or layer, it may be directly on, engaged, connected or coupled to the other element or layer, or intervening elements or layers may be present. In contrast, when an element is referred to as being “directly on,” “directly engaged to,” “directly connected to,” or “directly coupled to” another element or layer, there may be no intervening elements or layers present. Other words used to describe the relationship between elements should be interpreted in a like fashion (e.g., “between” versus “directly between,” “adjacent” versus “directly adjacent,” etc.). As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items.

Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

Spatially relative terms, such as “inner,” “outer,” “beneath,” “below,” “lower,” “above,” “upper,” and the like, may be used herein for ease of description to describe one element or feature's relationship to another element(s) or feature(s) as illustrated in the figures. Spatially relative terms may be intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as “below” or “beneath” other elements or features would then be oriented “above” the other elements or features. Thus, the example term “below” can encompass both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

With reference to FIGS. 1 and 2 , the turbocharger 20 includes a housing 22, a shaft 24, a turbine wheel 26, and a compressor wheel 28. The shaft 24 has an outer surface 29 and is rotatable with respect to the housing 22 and defines a centerline 30. Both the turbine wheel 26 and the compressor wheel 28 are mounted to the shaft 24. The shaft 24 may be a one-piece shaft 24, or alternatively may be split into multiple segments, such as a turbine segment and a compressor segment. The shaft 24 may optionally include a threaded end 31. The housing 22 includes a turbine section 32 and a compressor section 34. A bearing pack 35 is positioned between the turbine and compressor sections 32, 34 of the housing 22 for rotatably supporting the outer surface 29 of the shaft 24. The turbine section 32 of the housing 22 includes an exhaust inlet 36 that is radially spaced from the centerline 30 and an exhaust outlet 38 that is aligned with the centerline 30. The exhaust inlet 36 and the exhaust outlet 38 are configured to bolt to portions of the exhaust system of the internal combustion engine (not shown). Exhaust gases enter the housing 22 through the exhaust inlet 36 and exit the housing 22 through the exhaust outlet 38. The turbine wheel 26 is disposed in the turbine section 32 of the housing 22 and includes a plurality of turbine blades 40 with leading edges 42 that face the exhaust outlet 38. The flow of exhaust gas pushes against the turbine blades 40, which drives rotation of the turbine wheel 26.

The compressor section 34 of the housing 22 includes an air inlet 44 that is aligned with the centerline 30 and an air outlet 46 that is radially spaced from the centerline 30. The air inlet 44 is configured to receive air from the surrounding environment either directly or through an intake system (not shown). The air outlet 46 is configured to be connected to an intake manifold of the internal combustion engine via an inlet conduit (not shown), which may optionally include an intercooler (not shown). The compressor wheel 28 is disposed in the compressor section 34 of the housing 22 and includes a plurality of compressor blades 48 with leading edges 42′ that face the air inlet 44. Rotation of the turbine wheel 26 drives rotation of the compressor wheel 28 via the shaft 24. The compressor blades 48 pump air through the compressor section 34 of the housing 22 as the compressor wheel 28 rotates and discharge the air through the air outlet 46 at a higher pressure (boost) for delivery to the internal combustion engine.

With additional reference to FIG. 3 , typical turbine or exhaust wheels 50 (used interchangeably herein) are generally manufactured using high temperature alloys (e.g., Inconel) to withstand the heat and pressure that turbine or exhaust wheels 50 are exposed to by the exhaust flowing through the turbine section 32 of the turbocharger housing 22. Typical exhaust temperatures at the exhaust inlet 36 of a turbocharger 20 range from 1,000 to 2,000 degrees Fahrenheit. Turbine or exhaust wheels 50 are manufactured either by casting or machining a forged alloy. During manufacturing, a hub 52 is used as a means to hold or clamp the turbine or exhaust wheel 50 in place. For example, the hub 52 is used to hold the turbine or exhaust wheel 50 when it is fused or friction welded to the shaft 24. The hub 52 is generally large and left in place throughout the manufacturing process, the finishing process, and the final turbocharger assembly process. The hub 52 on traditional turbine or exhaust wheels 50 obstructs fluid flow through the turbine section 32 of the housing 22 and therefore limits the horsepower potential of the turbocharger 20.

In accordance with the subject disclosure, the hub 52 on the turbine or exhaust wheel 50 is removed and/or eliminated and the turbine blades 40 are re-shaped to an optimal geometry to create turbine wheel 26 (see FIGS. 4 and 5 ). This change decreases weight, increases surface area, provides increased exhaust-to-blade contact and therefore increases the efficiency and power output of the turbocharger 20. Removing the hub 52 and manipulating the fluid flow provides a significant horsepower increase and efficiency advantage for all turbochargers.

With reference to FIGS. 4 and 5 , the turbine wheel 26 of the turbocharger 20 includes a turbine body 54 that extends along the centerline 30 between a leading end 56 and a trailing end 58. The turbine body 54 has an outer circumference 60 that is radially spaced from the centerline 30 by a turbine radius 62. The turbine blades 40 are positioned on the turbine body 54. The turbine blades 40 have leading edges 42 that converge at a turbine apex 64 located at the leading end 56 of the turbine body 54. The turbine apex 64 is aligned with the centerline 30. The leading edges 42 of the turbine blades 40 extend helically from an inboard point 66 to an outboard point 68. In one configuration, the inboard points 66 of the leading edges 42 touch one another and form a pointed shape at the turbine apex 64. In another configuration, the inboard points 66 of the leading edges 42 are positioned closer to the centerline 30 than the smallest radius 69 of the shaft 24. In other words, the inboard points 66 of the leading edges 42 are positioned within an imaginary circle 70 drawn around the centerline 30 that has a radius 71 equal to the smallest radius 69 of the shaft 24. The imaginary circle 70 therefore coincides with the outer surface 29 of the shaft 24 and the inboard points 66 of the leading edges 42 are positioned either on the centerline 30 itself or radially between the centerline 30 and the imaginary circle 70.

With reference to FIGS. 6-8 , typical compressor or intake wheels 72 (used interchangeably herein) are generally cast or machined out of a solid forging (i.e., aluminum, titanium, etc.). The compressor or intake wheel 72 has a nut 74 (hub) at its center-point. This nut 74 is used in the final assembly process and/or when building or servicing the turbocharger 20. The nut 74 on the compressor or intake wheel 72 is used to secure the compressor or intake wheel 72 to the shaft 24 during final assembly. This nut 74 also creates an obstruction to airflow and limits the horsepower potential of the turbocharger 20, especially in racing or high horsepower, high rpm, high engine speed (i.e., high rpm), and high boost applications.

In accordance with the subject disclosure, the nut 74 on the compressor or intake wheel 72 is removed and/or eliminated and the compressor blades 48 are re-shaped to an optimal geometry to create compressor wheel 28.

With reference to FIGS. 9-11 , the compressor wheel 28 of the turbocharger 20 includes a compressor body 76 that extends along the centerline 30 between a leading end 56′ and a trailing end 58′. The compressor body 76 has an outer circumference 60′ that is radially spaced from the centerline 30 by a compressor radius 78. The compressor blades 48 are positioned on the compressor body 76. The compressor blades 48 have leading edges 42′ that converge at a compressor apex 80 located at the leading end 56′ of the compressor body 76. The compressor apex 80 is aligned with the centerline 30. The leading edges 42′ of the compressor blades 48 extend helically from an inboard point 66′ to an outboard point 68′. In one configuration, the inboard points 66′ of the leading edges 42′ touch one another and form a pointed shape at the compressor apex 80. In another configuration, the inboard points 66′ of the leading edges 42′ are positioned closer to the centerline 30 than the smallest radius 69 of the shaft 24. In other words, the inboard points 66′ of the leading edges 42′ are positioned within an imaginary circle 70′ drawn around the centerline 30 that has a radius 71′ equal to the smallest radius 69 of the shaft 24. The imaginary circle 70′ therefore coincides with the outer surface 29 of the shaft 24 and the inboard points 66′ of the leading edges 42′ are positioned radially between the centerline 30 and the imaginary circle 70′.

Alternative configurations for attachment of the compressor wheel 28 to the shaft 24 are provided, where a set screw 82, such as a hex screw, Allen screw, or similar style through-bore fastener, is threaded into the compressor wheel 28. The nut 74 is eliminated and therefore does not interfere with airflow. This provision decreases weight, increases potential horsepower, air-flow, boost pressure, and compressor speed.

In the illustrated examples, both the turbine wheel 26 and the compressor wheel 28 have a plurality of blades 40, 48 with leading edges 42, 42′ that converge at apexes 64, 80 that are aligned with the centerline 30. However, it should be appreciated that other configurations are possible where only the turbine wheel 26 is provided with an apex 64 or where only the compressor wheel 28 is provided with an apex 80. The apexes 64, 80 may be formed by either removing the hex nut 74, hub 52, or other manufacturing fixture from the leading ends 56, 56′ of the turbine or exhaust wheel 50 and/or the compressor or intake wheel 72 prior to assembly or by eliminating the hex nut 74, hub 52, or other manufacturing fixture altogether from the manufacturing process. Regardless, the turbine wheel 26 and/or the compressor wheel 28 in final assembled form have a nut-less/hub-less configuration, meaning that there is no nut 74 or hub 52 adjacent to the leading ends 56, 56′ of the turbine wheel 26 and the compressor wheel 28.

Although other configurations are possible, in the illustrated example, the turbine wheel 26 is welded to the shaft 24 while the compressor wheel 28 is attached to the shaft 24 by a threaded connection 84 and set screw 82 (shown in FIG. 10 ). The compressor wheel 28 includes a through-bore 86 with multiple stepped portions 88, 90, 92. The first stepped portion 88 has a smooth, cylindrical shape and receives a portion of the shaft 24. The second stepped portion 90 is threaded and threadably engages the threaded end 31 of the shaft 24. The third stepped portion 92 is also threaded and threadably engages the set screw 82. The third stepped portion 92 has a diameter that is smaller than a diameter of the second stepped portion 90 and the diameter of the second stepped portion 90 is smaller than a diameter of the first stepped portion 88. The threads in the second and third stepped portions 90, 92 run in opposite directions. For example, the second stepped portion 90 may be provided with left-hand threads while the third stepped portion 92 may be provided with right-hand threads, or vice versa. The through-bore 86 also includes an end portion 94 adjacent to the compressor apex 80 that has hexagonally-shaped internal walls (i.e., a hex recess) that are configured to receive a tool for tightening the compressor wheel 28 on the threaded end 31 of the shaft 24. A tool pathway 96 extends along the centerline 30 between the third stepped portion 92 and the end portion 94. The tool pathway 96 provides tool access to the set screw 82, which prevents the compressor wheel 28 from becoming over-tightened (i.e., over torqued) on the threaded end 31 of the shaft 24. As a result, the turbine apex 64 and/or the compressor apex 80 are unobstructed by a nut 74, hub 52, or other fastener. It should be appreciated that this arrangement may be reversed where the compressor wheel 28 is welded to the shaft 24 and the turbine wheel 26 is connected to the shaft 24 by set screw 82 and threaded connection 84. Alternatively, both the turbine wheel 26 and the compressor wheel 28 may be connected to the shaft 24 via respective set screws 82 and threaded connections 84.

A method of constructing the turbocharger 20 described above is also provided. The method includes the steps of: machining a turbine wheel 26 having a plurality of turbine blades 40, machining a compressor wheel 28 having a plurality of compressor blades 48, creating leading edges 42, 42′ on the plurality of turbine blades 40 and the plurality of compressor blades 48, and performing a finishing operation on the turbine wheel 26 and/or the compressor wheel 28 to form apexes 64, 80 where the leading edges 42, 42′ converge. The finishing operation may include removing a nut 74, hub 52, or other manufacturing/machining fixture from the turbine or exhaust wheel 50 and/or the compressor or intake wheel 72 and extending the leading edges 42, 42′ towards a centerline 30 of the turbine wheel 26 and/or the compressor wheel 28. As an alternative to machining the turbine wheel 26 and the compressor wheel 28, the turbine wheel 26 and the compressor wheel 28 can be cast, forged, or milled into the appropriate shape.

Optionally, the method may include the additional step of mounting the turbine wheel 26 and/or the compressor wheel 28 to a shaft 24 using a welding operation so that the apexes 64, 80 are unobstructed by a nut 74, hub 52, or other fastener. Alternatively, the method may include additional steps of mounting the turbine wheel 26 and/or the compressor wheel 28 to a shaft 24 using a countersunk set screw 82 so that the apexes 64, 80 are unobstructed by a nut 74, hub 52, or other fastener. In accordance with this method of attachment, the set screw 82 is threaded into the third stepped portion 92 of the through-bore 86 of the compressor wheel 28. The threaded end 31 of the shaft 24 is then threaded into the second stepped portion 90 of the through-bore 86. A tool (such as a hex tool) is inserted into the end portion 94 and the tool pathway 96 of the through-bore 86 to set the depth of the set screw 82 in the third stepped portion 92 of the through-bore 86. A larger hex tool (e.g., an Allen key) is inserted into the end portion 94 of the through-bore 86 to rotate the compressor wheel 28 relative to the shaft 24 until the threaded end 31 of the shaft 24 tightens against the set screw 82. Advantageously, this attachment mechanism between the compressor wheel 28 and the shaft 24 is easy to loosen/disassemble, even after extended periods of turbocharger use. This is an improvement over existing designs, where the high-speed rotation of the compressor wheel 28 during turbocharger operation over-tightens (i.e., over-torques) the compressor wheel 28 on the threaded end 31 of the shaft 24 making it difficult to disassemble. The set screw 82 in the subject design stops further tightening of the compressor wheel 28 on the threaded end 31 of the shaft 24 during use. The set screw 82 also prevents over-torqueing of the compressor wheel 28 on the shaft 24 during or after assembly, which can bend the shaft 24 and create wobble in the turbocharger 20 and damage the bearing pack 35 and/or the turbocharger 20.

Eliminating the nut 74 and/or hub 52 on both the turbine or exhaust wheel 50 and the compressor or intake wheel 72 greatly improves fluid flow and in-turn increases the potential horsepower and efficiency of the turbocharger 20. This manufacturing change is applicable to all wheel sizes, frame sizes, and area/radius (A/R) combinations for all turbocharger applications. The result is a dual apex turbocharger 20 with decreased weight and increased speed capability.

FIGS. 12 and 13 illustrate an alternative design for a compressor wheel 28″ of the turbocharger 20. The compressor wheel 28″ includes a plurality of compressor blades 48″ that extend from an exducer plate 98″ at a trailing end 58″ of the compressor wheel 28″. The exducer plate 98″ has a disc-like shape and defines an outer circumference 60″ of the compressor wheel 28″. The compressor blades 48″ have leading edges 42″ that converge at a compressor apex 80″ located at a leading end 56″ of the compressor wheel 28″. The compressor apex 80″ is aligned with a centerline 30″ of the compressor wheel 28″. The leading edges 42″ of the compressor blades 48″ extend helically from an inboard point 66″ to an outboard point 68″. In the illustrated example, the inboard points 66″ of the leading edges 42″ touch one another and form a pointed shape at the compressor apex 80″. In other words, the leading edges 42″ of the compressor blades 48″ intersect at the compressor apex 80″. Because the compressor apex 80″ is pointed and free of a tool interface, the flow characteristics and associated performance of the compressor wheel 28″ is enhanced. As will be explained in greater detail below, the exducer plate 98″ includes one or more through bores 100″ to facilitate installation and removal of the compressor wheel 28″ relative to the shaft 24. The through bores 100″ extend through the compressor wheel 28″ at locations that are offset (i.e., radially spaced) from the centerline 30″. Of course, it should be appreciated that the compressor wheel 28″ shown in FIG. 12 includes an internally threaded bore much like the bore 86 of the compressor wheel 28 shown in FIG. 10 , except that the internally threaded bore in the compressor wheel 28″ shown in FIG. 12 may or may not extend all the way to the leading end 56″ of the compressor wheel 28″.

FIG. 13 illustrates a backing plate 102″, which is a sub-component of the housing 22 shown in FIG. 1 , which is sometimes referred to as the “center housing rotation assembly” or “CHRA.” The backing plate 102″ has a disc-like shape and includes a center hole 104″ that receives a portion of the shaft 24. The backing plate 102″ may also include a circular depression 106″ that receives a portion of the exducer plate 98″ of the compressor wheel 28″. During operation of the turbocharger 20, the backing plate 102″ remains stationary while both the shaft 24 and the compressor wheel 28″ rotate relative to the backing plate 102″. The backing plate 102″ further includes one or more holes 108″ that align with the through bores 100″ in the exducer plate 98″ of the compressor wheel 28″ when the compressor wheel 28″ is rotated to a predefined angular position. This allows for the insertion of one or more fixation members 110″, such as dowel pins, set screws, other fasteners, or a tool, into both the holes 108″ in the backing plate 102″ and the through bores 100″ in the compressor wheel 28″ to temporarily lock rotation of the compressor wheel 28″ relative to the backing plate 102″, thus creating a temporary fixation mechanism between the compressor wheel 28″ and the housing 22. Although other configurations are possible, in the illustrated example, the holes 108″ in the backing plate 102″ and the through bores 100″ in the compressor wheel 28″ are arranged 180 degrees apart from one another and have equal diameters. Additionally, the holes 108″ in the backing plate 102″ and/or the through bores 100″ in the compressor wheel 28″ may be internally threaded to accept fasteners as the fixation members 110″.

Manufacturers or service technicians can grasp the other end of the shaft 24 and turn it clockwise or counter-clockwise to either tighten or loosen the compressor wheel 28″ from the shaft 24. This design and associated assembly/disassembly process allows for easy installation and removal of the compressor wheel 28″ from the shaft 24 without compromising or damaging the compressor blades 48″ or other parts of the compressor wheel 28″. It also eliminates the need for a nut, nose, or other tool interface at the leading end 56″ of the compressor wheel 28″; however, it should be appreciated that this configuration is applicable to both nose-less compressor wheels and compressor wheels that include a nose at the leading end.

As shown in FIG. 14 , the compressor wheel 28″ illustrated in FIG. 12 can alternatively be installed on and removed from the shaft 24 using a tool 112″. The tool 112″ includes two posts 114″ that are configured (i.e., have a size, shape, and spacing) to be received in the two through bores 100″ in the exducer plate 98″ of the compressor wheel 28″ in sliding engagement. The tool 112″ also has a tool body 116″ with a center point 118″ that is bisected by the centerline 30″ when the tool 112″ is brought into alignment with the compressor wheel 28″. A socket interface 120″, positioned at a center point 118″ of the tool 112″, extends into the tool body 116″ and is configured to couple the tool 112″ to a wrench or breaker bar (not shown). This allows the tool 112″ to be rotated related to the shaft 24 and exert a rotational force to the compressor wheel 28″ without applying any pressure of the compressor blades 48″. Although other configurations are possible, in the illustrated example, the through bores 100″ in the compressor wheel 28″ and the posts 114″ on the tool 112″ are arranged 180 degrees apart from one another and have substantially equal diameters.

When the posts 114″ on the tool 112″ are inserted into the through bores 100″ in the compressor wheel 28″, the tool 112″ and the compressor wheel 28″ are temporarily locked in rotation with each other. Manufacturers or service technicians can hold/clamp the shaft 24 in place and turn the tool 112″ in a first (e.g. clockwise) direction and a second (e.g., counter-clockwise) direction to either thread (i.e., tighten) or unthread (i.e., loosen) the compressor wheel 28″ from the shaft 24. This design and associated assembly/disassembly process allows for easy installation and removal of the compressor wheel 28″ from the shaft 24 without compromising or damaging the compressor blades 48″ or other parts of the compressor wheel 28″. It also eliminates the need for a nut, nose, or other tool interface at the leading end 56″ of the compressor wheel 28″; however, it should be appreciated that this configuration is applicable to both nose-less compressor wheels and compressor wheels that include a nose at the leading end.

FIGS. 15 and 16 illustrate an alternative design for a compressor wheel 28″ and associated tool 112′″. The compressor wheel 28″ includes a plurality of compressor blades 48″ that extend from an exducer plate 98″ at a trailing end 58′ of the compressor wheel 28′. The exducer plate 98′ has a disc-like shape and defines an outer circumference 60′″ of the compressor wheel 28′. The compressor blades 48″ have leading edges 42″ that converge at a compressor apex 80′″ located at a leading end 56″ of the compressor wheel 28′. The compressor apex 80′″ is aligned with a centerline 30′″ of the compressor wheel 28′. The leading edges 42″ of the compressor blades 48″ extend helically from an inboard point 66″ to an outboard point 68′. In the illustrated example, the inboard points 66″ of the leading edges 42″ touch one another and form a pointed shape at the compressor apex 80′″. In other words, the leading edges 42″ of the compressor blades 48″ intersect at the compressor apex 80′″. Because the compressor apex 80′″ is pointed and free of a tool interface, the flow characteristics and associated performance of the compressor wheel 28″ is enhanced. The exducer plate 98″ includes three through bores 100′″ to facilitate installation and removal of the compressor wheel 28″ relative to the shaft 24. The through bores 100′″ extend through the compressor wheel 28″ at locations that are offset (i.e., radially spaced) from the centerline 30′″. Of course, it should be appreciated that the compressor wheel 28″ shown in FIG. 15 includes an internally threaded bore much like the bore 86 of the compressor wheel 28 shown in FIG. 10 , except that the internally threaded bore in the compressor wheel 28″ shown in FIG. 12 may or may not extend all the way to the leading end 56″ of the compressor wheel 28′.

As shown in FIG. 16 , the compressor wheel 28″ illustrated in FIG. 15 can be installed on and removed from the shaft 24 using tool 112′″. The tool 112′ includes three posts 114′″ that are configured (i.e., have a size, shape, and spacing) to be received in the three through bores 100′″ in the exducer plate 98′ of the compressor wheel 28″ in sliding engagement. Like in the other design, the tool 112′″ has a tool body 116′″ with a center point 118′″ that is bisected by the centerline 30′ when the tool 112′″ is brought into alignment with the compressor wheel 28′. A socket interface 120′″ is positioned at a center point 118′″ of the tool 112′″, extends through the tool body 116′″, and is configured to couple the tool 112′″ to a wrench or breaker bar (not shown). This allows the tool 112′″ to be rotated related to the shaft 24 and exert a rotational force to the compressor wheel 28′ without applying any pressure of the compressor blades 48′. Although other configurations are possible, in the illustrated example, the through bores 100′″ in the compressor wheel 28″ and the posts 114′″ on the tool 112′″ are arranged 120 degrees apart from one another and have substantially equal diameters.

Like in the previous design, when the posts 114′″ on the tool 112′″ are inserted into the through bores 100′ in the compressor wheel 28′, the tool 112′″ and the compressor wheel 28″ are temporarily locked in rotation with each other. Manufacturers or service technicians can hold/clamp the shaft 24 in place and turn the tool 112′″ in a first (e.g. clockwise) direction and a second (e.g., counter-clockwise) direction to either thread (i.e., tighten) or unthread (i.e., loosen) the compressor wheel 28″ from the shaft 24. This design and associated assembly/disassembly process allows for easy installation and removal of the compressor wheel 28″ from the shaft 24 without compromising or damaging the compressor blades 48″ or other parts of the compressor wheel 28″. It also eliminates the need for a nut, nose, or other tool interface at the leading end 56″ of the compressor wheel 28′″; however, it should be appreciated that this configuration is applicable to both nose-less compressor wheels and compressor wheels that include a nose at the leading end. The designs disclosed herein advantageously provide more power using the same footprint. Because output can be increased without increasing the frame size and A/R of the housing 22, the subject disclosure is particularly useful when there are space limitations on the packaging dimensions of the turbocharger 20 (e.g., where the turbocharger 20 fits between the cylinder banks of the internal combustion engine) or in motorsports applications with class restrictions and rules that limit wheel size and other size dimensions of the turbocharger 20.

Many modifications and variations of the subject matter disclosed herein are possible in light of the above teachings and may be practiced otherwise than as specifically described while within the scope of the appended claims. It should be appreciated that variations of the disclosed designs are possible without completely eliminating the hex nut 74 or the hub 52. For example and without limitations, the size of the nut 74 or hub 52 may be reduced and/or the nut 74 or hub 52 may be coned to form the apexes 64, 80. 

What is claimed is:
 1. A forced induction device for an internal combustion engine, comprising: a compressor wheel having an internally threaded bore; a shaft extending co-axially about a centerline, the shaft having a threaded end that threads into the internally threaded bore of the compressor wheel to threadably mount the compressor wheel to the shaft; at least one through bore extending through the compressor wheel at a location that is offset from the centerline of the shaft; and a tool including at least one post that is configured to be received in the through bore in the compressor wheel so as to temporarily lock the tool in rotation with the compressor wheel and allow the compressor wheel to be rotated relative to the shaft during installation and removal of the compressor wheel.
 2. The forced induction device as set forth in claim 1, wherein the compressor wheel has a plurality of blades with leading edges that converge at an apex that is aligned with the centerline of the shaft.
 3. The forced induction device as set forth in claim 2, wherein the leading edges of the plurality of blades extend helically from an inboard point to an outboard point.
 4. The forced induction device as set forth in claim 3, wherein the inboard points of the leading edges touch one another and form a pointed shape at the apex.
 5. The forced induction device as set forth in claim 3, wherein the shaft has a radius and the inboard points of the leading edges are positioned closer to the centerline than the radius of the shaft.
 6. The forced induction device as set forth in claim 1, wherein the compressor wheel includes an exducer plate and the at least one through bore in the compressor wheel extends through the exducer plate at a location that is radially spaced from the centerline of the shaft.
 7. The forced induction device as set forth in claim 6, wherein the tool includes a socket interface, positioned at a center point of the tool, that is configured to couple the tool to a wrench, ratchet, Allen key, or breaker bar.
 8. The forced induction device as set forth in claim 6, wherein the compressor wheel includes two through bores that are arranged 180 degrees apart from one another and wherein the tool includes two posts that are arranged 180 degrees apart from one another and are configured to be received in the through bores in the compressor wheel.
 9. The forced induction device as set forth in claim 6, wherein the compressor wheel includes three through bores that are arranged 120 degrees apart from one another and wherein the tool includes three posts that are arranged 120 degrees apart from one another and are configured to be received in the through bores in the compressor wheel.
 10. A forced induction device for an internal combustion engine, comprising: a shaft extending co-axially about a centerline; a compressor wheel threadably mounter to the shaft; a turbine wheel mounted to the shaft; a housing that includes a turbine section for housing the turbine wheel and a compressor section for housing the compressor wheel, wherein the shaft is rotatably supported by the housing; at least one through bore extending through the compressor wheel at a location that is offset from the centerline of the shaft; and a tool including at least one post that is configured to be received in the through bore in the compressor wheel so as to temporarily lock the tool in rotation with the compressor wheel and allow the compressor wheel to be rotated relative to the shaft during installation and removal of the compressor wheel.
 11. The forced induction device as set forth in claim 10, wherein both the turbine wheel and the compressor wheel have a hub-less configuration and each have an apex that is unobstructed by a nut or other fastener. 